US5088898A - Reciprocating pump - Google Patents
Reciprocating pump Download PDFInfo
- Publication number
- US5088898A US5088898A US07/596,718 US59671890A US5088898A US 5088898 A US5088898 A US 5088898A US 59671890 A US59671890 A US 59671890A US 5088898 A US5088898 A US 5088898A
- Authority
- US
- United States
- Prior art keywords
- pump
- stroke
- discharge
- pump section
- sections
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
- F04B43/10—Pumps having fluid drive
- F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
- F04B43/1136—Pumps having fluid drive the actuating fluid being controlled by at least one valve with two or more pumping chambers in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
Definitions
- the invention relates to reciprocating pumps having a plurality of pump sections, each pump section having a reciprocating action element, such as a bellows or diaphragm. More particularly, the present invention relates to control of the action elements in pumps having plural pump sections, the control being such that at least one pump section is discharging into a common pump discharge passageway at all times.
- Bellows or diaphragm pumps having a single pump section are well known in the art.
- the discharge and suction strokes are alternately produced by the reciprocating motion of the pump action element, i.e. the diaphragm or bellows.
- the pump action element i.e. the diaphragm or bellows.
- pulses of fluid are discharged from the pump and the pressure of the fluid being discharged from such pumps varies greatly.
- Such variations are undesirable in that they can cause pipe connections on the discharge side of the pump to be loosened, or cause "knocking" of the pipes thereby creating undesired noise
- the variations in pressure can cause impurities which may accumulate on the interior wall of the discharge pipe to be peeled therefrom.
- the pressure variations can cause enlargement of the filter openings thus lowering the capture rating of the filter.
- bellows or diaphragm pumps having a pair of pump sections with the pump action elements of the two sections being interlocked so that a discharge stroke of one pump section coincides with a suction stroke of the other pump section.
- Such pumps may have a common discharge passageway and a common suction passageway for the two pump sections. It would at first appear that since one pump section executes a discharge stroke while the other executes a suction stroke, or vice versa, there would be a continuous discharge hence fairly constant pressure should be present in the discharge passageway. However, this is not true in actual practice since it takes the action elements a finite time to stop and change direction. During this change-over interval, which occurs at the same time for both pump section, the pressure in the discharge passageway drops drastically. As a result, there are large pressure variations in the discharge passageway with the same undesirable consequences mentioned above.
- An object of the present invention is to provide a novel method and apparatus for controlling a reciprocating pump having a plurality of pump sections with a common discharge passageway whereby a substantially continuous discharge of fluid is provided at the discharge side of the pump.
- An object of the present invention is to provide a novel method and apparatus for controlling a reciprocating pump having a plurality of pump sections with a common discharge so that pressure variations at the discharge side of the pump are substantially reduced.
- An object of the present invention is to provide an improvement in reciprocating pumps of the type having a plurality of pump sections, each of the pump sections including a reciprocating action element movable in first and second directions to define suction and discharge strokes of the pump section, each stroke being separated from a following stroke by a change-over interval, each pump section having a discharge outlet connected to a common discharge passageway for the pump and a suction inlet connected to a common supply passageway for the pump, the improvement comprising a drive control for driving the action elements so that when at least one of the pump sections is in a suction stroke or a change-over interval at least one other of the pump sections is in a discharge stroke.
- the pump sections are interconnected in pairs to form composite pump sections wherein one pump section of a composite pump section is in a discharge stroke when the other pump section of the composite pump section is in a suction stroke.
- the drive control drives the action elements to initiate strokes one at a time at intervals of T/N where T is the time it takes a composite pump section to complete a stroke and N is the number of composite pump sections.
- a further object of the present invention is to provide a novel method of operating a reciprocating pump of the type described above, the method comprising driving the action elements so that at any instant at least one of the pump sections is discharging into the common discharge passageway of the pump.
- FIG. 1 is a sectional view of a pump taken along the line I--I of FIG. 2, the pump having three composite pump sections;
- FIG. 2 is a sectional view of a composite pump section taken along the line II--II of FIG. 1;
- FIG. 3 is a sectional view showing an alternative pump section construction
- FIG. 4 is a timing diagram illustrating the relative timings of the discharge and suction strokes of three pump sections driven in accordance with the present invention
- FIG. 5 is a plot of the discharge pressure of the pump shown in FIG. 1 and controlled in accordance with the present invention
- FIG. 6 is a plot of the discharge pressure of the pump shown in FIG. 1 when the action elements are driven in unison;
- FIG. 7 is a plot of the discharge pressure of the pump shown in FIG. 1 when the action element of only one composite pump section is driven.
- FIGS. 1 and 2 illustrate a preferred embodiment of the invention wherein a bellows type reciprocating pump 1 is pneumatically actuated by control signals produced by a controller 2.
- the pump 1 has a pump casing 3.
- a head wall 4 extends vertically as viewed in FIG. 1 to divide the interior of the casing into first and second parts.
- Four cylinder walls 5 extend from the head wall 4 to the casing 3 to further divide the interior of the pump casing into a plurality of pump sections la.
- the interior of the pump casing 3 is thus divided into three composite pump sections 1 1 , 1 2 and 1 3 with each composite pump section having a pair of pump sections 1a.
- Each pump section has a pump chamber 6 and a bellows 7.
- bellows 7 is provided with a peripheral recess 7a for receiving a gasket 8.
- the head wall 4 is provided with an annular recess for receiving the gasket 8 and the open end of bellows 7, and an annular clamp 9 secures the gasket and bellows to the head wall.
- the bellows 7 therefore hermetically divides pump chamber 6 into a pump action chamber 6a within the bellows and a pump operation chamber 6b outside the bellows.
- the free end of bellows 7 has a peripheral flange 7b which is clamped to an action plate 11 by an annular clamp plate 10.
- the pair of bellows 7 in each of the composite pump sections 1 1 , 1 2 and 1 3 are mechanically interconnected so as to move in synchronism.
- the connecting means comprises a plurality of rods 12 only one of which is shown in FIG. 2.
- the rods 12 are threaded at both ends and bolted to the action plates 11 to which the bellows are clamped.
- Each rod 12 extends through head wall 4 and is free to reciprocate therein.
- An O-ring 13 surrounds each rod and serves to seal the chamber 6b in one pump section 1a from the chamber 6b of the other pump section.
- the length of rods 12 is chosen such that when one bellows 7 of a composite pump section is fully extended the other bellows of that composite pump section is in its most contracted state.
- the headwall 4 has a plurality of passageways formed therein including a fluid discharge passageway 14 and a suction or fluid supply passageway 15.
- the fluid supply passageway 15 is connected to a source of fluid to be pumped, this source being indicated at 17 in FIG. 1.
- the supply passageway has a plurality of branch passageways 15a, each of which is connected through a respective check valve 20 to the pump action chamber 6a inside a respective bellows 7.
- the check valves 20 permit the flow of fluid from the supply passageway to the pump action chambers 6a.
- each bellows 7 is connected through a check valve 19 and a branch passageway 14a to the discharge passageway 14 so that all pumped fluid is discharged from the pump through check valves 19 and passageway 14 to external piping indicated generally at 16 in FIG. 1.
- the check valves 19 and 20 may be completely separate valves as illustrated in FIG. 2 or the check valves 19 and 20 for a given pump section la may be integrally formed as shown in FIG. 3 so as to have a single monolithic valve body.
- Each pump section 1a is provided with a fluid leakage detector 18 for detecting the leakage of fluid from the pump action chamber 6a to the pump operation chamber 6b.
- Each composite pump section is driven by alternately applying a fluid pressure to the pump action chamber 6b of one of its pump sections 1a while connecting the chamber 6b of the other pump section to an exhaust, and then reversing the connections.
- the arrows 21a represent pipes or fluid conduits and the direction of flow of fluid therein at a particular instant in time.
- FIG. 2 depicts the position of a composite valve section as it completes a stroke. During this stroke fluid pressure has been applied to the chamber 6b on the left side of the FIGURE through one pipe 21a while the chamber 6b on the right side has been exhausted. The fluid pressure in left chamber 6b has compressed the left bellows 7 so as to force fluid from the chamber 6a through the left check valve 19 into the discharge passageway 14. At the same time, the right bellow 7 has been expanded thereby creating a suction in the right chamber 6a to draw fluid from supply passageway 15 through the right check valve 20 and into the chamber.
- each pump section la has a suction stroke during which fluid is drawn into the chamber 6a from the supply passageway 15 and a discharge stroke during which fluid is discharged from chamber 6a into the discharge passageway 14. Between each stroke is a change-over interval.
- the pump described above was tested under the following conditions. Fresh water at 25° C. was supplied to the pump through passageway 15 and pressurized air at 4kgf/cm 2 was selectively applied to the chambers 6b of only one composite pump section. This resulted in a stroke rate of 50 strokes per minute with the stroke time T being about 0.6 sec.
- the discharge pressure in the discharge passageway 14 was monitored and plotted, yielding a curve as shown in FIG. 7. During the change-over intervals between strokes, the discharge pressure drops almost to zero with peaks of pressure occurring at the end of each stroke. In FIG. 7, alternate pressure peaks are produced during the discharge stroke of one pump section 1a and the intervening peaks are produced by the discharge stroke of the other pump section. This accounts for the differences in magnitude of adjacent peaks.
- pressure pulses The variations in pressure (i.e. pressure pulses) occurring in the discharge passageway 14 cause various problems in systems downstream of passageway 14 depending on the type of system to which the pump is connected.
- the pressure pulses can cause pipe vibration with attendant noise, enlarge filter openings, or dislodge accumulated deposits from the interior of pipes.
- operation of one of the composite pump sections is used as a reference for timing the initiation of the strokes of the other composite pump sections so that at any instant in time at least one composite pump section is in a discharge stroke.
- the operation is such that when any one of the composite pump sections is in a change-over interval, at least one of the other two composite pump sections is in a discharge stroke. Since at least one composite pump section will be discharging into discharge passageway 14 at any given time, the pressure in the discharge passageway will never drop below the peak values shown in FIG. 7.
- the pressure in discharge passageway 14 may be maintained at a level greater than the highest peak value in FIG. 7 with relatively small pressure pulses. This is illustrated in FIG. 5.
- composite pump section 1 1 is selected.
- composite pump section 1 1 is provided with left and right sensors 22a mounted in the pump casing 3.
- One sensor is mounted so as to sense the right action plate 11 and produce an output signal when the right bellows 7 moves away from its fully extended position.
- the other sensor performs a similar function with respect to the left action plate 11 and left bellows 7.
- the composite pump section 1 1 is in the position illustrated in FIG. 2 at the time conduit fluid pressure is applied through the right fluid conduit 21a.
- the sensor produces an output signal indicating the starting of a composite pump section stroke.
- the left sensor 22a senses the presence of the left action plate 11 and produces an output signal indicating the end of the stroke.
- pressurized fluid is applied over the left fluid conduit 21a to the left chamber 6b, the left action plate moves away from left sensor 22a and it produces a second signal indicating the start of another stroke of the composite pump section. The end this stroke is signalled by the right sensor 22a when the right action plate again reaches the position shown in the drawing.
- the right sensor 22a signals the beginning of a stroke of composite pump section 11 as it moves to the left and the end of the next stroke as the composite pump section moves to the right.
- Left sensor 22a signals the end of a stroke to the left and the beginning of a stroke to the right.
- the output signals from the right and left sensors are applied to a control synchronizing circuit 2 which includes a delay control 22 and a plurality of pneumatic drives 21, 211.
- the signals from right and left sensors 22a are applied to the delay control 22.
- the delay control may be a microprocessor or any other conventional means for measuring the time interval T which elapses during one stroke of composite pump section 1 1 , dividing the measured interval by the number N of composite pump sections, and producing output signals at intervals of T/N. Since the embodiment shown has three composite pump sections the delay control produces two output signals, one at time T/3 and another at time 2T/3 after a stroke of composite pump section 1 is initiated. These two signals control the pneumatic drives 21.
- the pneumatic drives 21 are of conventional design and each includes a change-over valve and an electrical control circuit for actuating the changeover valve in response to signals from the delay control 22.
- Each change-over valve is connected to a source of pneumatic pressure, an exhaust port and the fluid conduits 21a which are connected to the right and left pump operating chambers 6b of a composite pump section controlled by the pneumatic drive.
- the arrangement is such that a source of air under pressure is connected to the left pump operating chamber 6b while the right pump operating chamber is connected to the exhaust port.
- the connections Upon occurrence of a change-over, initiated by a signal from delay control 22, the connections are reversed so that the left pump operating chamber is connected to the exhaust port and the right pump operating chamber is connected to the source of pressure. Since the pressure drives 21 are of conventional design and may take many forms, the details thereof are not shown in the drawing.
- the pneumatic drive 21 1 has a change-over valve connected as described above. However, because the outputs of pneumatic drive 21 1 are connected via conduits 21a to the composite pump section 1 1 which serves as the timing reference, its control circuit receives no signal from delay control 22. Instead, the control circuit in pneumatic drive 21 1 is freerunning and controls its associated change-over valve to change over at the end of each interval T where T represents a time at least equal to the time it takes the composite pump section 1 1 to make one stroke. Therefore, the change-over valve in pneumatic drive 21 1 repeatedly cycles so the composite pump section 1 1 is continuously driven through a stroke to the left followed after a change-over by a stroke to the right.
- FIG. 4 is a wave-form diagram illustrating the action of a single pump section 1a in each of the composite pump sections 1 1 , 1 2 and 1 3 . Since each composite pump section has two pump sections 1a which act in a complementary manner, it will be understood that the waveforms for the other pump sections will be the inverse of those shown. For purposes of the following discussion it will be assumed that the waveforms of FIG. 4 represent the discharge/suction of the right pump sections la in the three composite pump sections.
- the discharge pressure was measured and plotted, yielding a curve as shown in FIG. 5. The variations in pressure in the discharge were as small as 0.5 kgf/cm 2 .
- the principles of the invention may be implemented with structures other than those described. It is not necessary that the delay control be referenced to the stroke of one of the composite pump sections.
- the stroke of each composite pump section may be individually controlled to establish the optimum delay time that the conditions of pump operation permit. It is also possible to set a timer in advance to control the delay time. The only requirement is to insure that when any one composite pump section is in the change-over between stokes, at least one other composite pump section is discharging into the discharge passageway.
- the invention is not limited to use with bellows-type pumps but may be used equally well with diaphragm pumps and reciprocating pumps such as those having a reciprocating cylinder or piston.
- the pump need not have composite pump sections with complementary acting pump sections. Each pump section may be independently driven. In such a pump having n pump sections, the delay time t may theoretically be set within the range of 1.5T/N ⁇ t ⁇ T. However, because of the delay which occurs between generation of a delay control signal (as generated by delay control 22 in the described embodiment) and the actual time that a pump section is caused to move in response to that signal, the delay time may be set within the range T/N ⁇ t ⁇ T. This will insure that when any given pump section is in a suction stroke or a change-over interval at least one other pump section will be in a discharge stroke.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1317206A JPH03179184A (ja) | 1989-12-05 | 1989-12-05 | 往復動ポンプ |
JP1-317206 | 1989-12-05 |
Publications (1)
Publication Number | Publication Date |
---|---|
US5088898A true US5088898A (en) | 1992-02-18 |
Family
ID=18085648
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US07/596,718 Expired - Fee Related US5088898A (en) | 1989-12-05 | 1990-10-10 | Reciprocating pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US5088898A (de) |
EP (1) | EP0431753B1 (de) |
JP (1) | JPH03179184A (de) |
KR (1) | KR950003063B1 (de) |
DE (1) | DE69011634T2 (de) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6827479B1 (en) * | 2001-10-11 | 2004-12-07 | Amphastar Pharmaceuticals Inc. | Uniform small particle homogenizer and homogenizing process |
US6949202B1 (en) * | 1999-10-26 | 2005-09-27 | Reflectivity, Inc | Apparatus and method for flow of process gas in an ultra-clean environment |
US20100119394A1 (en) * | 2006-07-11 | 2010-05-13 | Bernhard Frey | Cylinder piston arrangement for a fluid pump or a fluid motor |
US20110150680A1 (en) * | 2009-12-22 | 2011-06-23 | Smith & Nephew, Inc. | Disposable Pumping System and Coupler |
CN106795876A (zh) * | 2014-08-08 | 2017-05-31 | 日本皮拉工业株式会社 | 波纹管泵装置 |
WO2019090388A1 (en) * | 2017-11-10 | 2019-05-16 | Quantum Servo Pumping Technologies Pty Ltd | Pumping systems |
US10408207B2 (en) | 2014-08-04 | 2019-09-10 | Nippon Pillar Packing Co., Ltd. | Bellows pump device |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04125685U (ja) * | 1991-05-07 | 1992-11-16 | 山口日本電気株式会社 | ベローズポンプ |
JPH08121342A (ja) * | 1994-10-26 | 1996-05-14 | Nippon Pillar Packing Co Ltd | 定量供給ポンプ |
US6079959A (en) * | 1996-07-15 | 2000-06-27 | Saint-Gobain Performance Plastics Corporation | Reciprocating pump |
KR100363748B1 (ko) * | 1998-10-26 | 2002-12-11 | 니폰 필라고교 가부시키가이샤 | 펌프의 맥동 감쇠장치 |
JP3205909B2 (ja) * | 1999-10-25 | 2001-09-04 | 日本ピラー工業株式会社 | 脈動低減装置付きポンプ |
JP3761754B2 (ja) | 1999-11-29 | 2006-03-29 | 日本ピラー工業株式会社 | ポンプ、アキュムレータ等の流体機器 |
US7284970B2 (en) | 1999-11-29 | 2007-10-23 | Nippon Pillar Packing Co., Ltd. | Fluid apparatus having a pump and an accumulator |
JP2001153053A (ja) | 1999-11-29 | 2001-06-05 | Nippon Pillar Packing Co Ltd | ベローズを有する流体機器 |
JP3610272B2 (ja) | 1999-11-29 | 2005-01-12 | 日本ピラー工業株式会社 | ベローズを有する流体機器 |
JP3577435B2 (ja) | 1999-11-29 | 2004-10-13 | 日本ピラー工業株式会社 | ベローズを有する流体機器 |
JP3399897B2 (ja) * | 2000-02-14 | 2003-04-21 | 日本ピラー工業株式会社 | ポンプ、アキュムレータ等の流体機器 |
JP3375930B2 (ja) | 2000-03-06 | 2003-02-10 | 日本ピラー工業株式会社 | チェックバルブ |
JP3874416B2 (ja) | 2003-05-02 | 2007-01-31 | 日本ピラー工業株式会社 | 往復動ポンプ |
US7335003B2 (en) | 2004-07-09 | 2008-02-26 | Saint-Gobain Performance Plastics Corporation | Precision dispense pump |
PL2482651T3 (pl) * | 2009-09-28 | 2016-04-29 | Dow Global Technologies Llc | Kompozycje dibromomalonamidu i ich zastosowanie jako biocydów |
CN103388577A (zh) * | 2012-05-09 | 2013-11-13 | 日本皮拉工业株式会社 | 液体用容积型泵 |
EP3115607B1 (de) * | 2015-07-10 | 2018-02-21 | J. Wagner AG | Doppelmembranpumpe |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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US2463552A (en) * | 1947-03-03 | 1949-03-08 | Donald H Newhall | High-pressure hydraulic system |
US4269569A (en) * | 1979-06-18 | 1981-05-26 | Hoover Francis W | Automatic pump sequencing and flow rate modulating control system |
US4836756A (en) * | 1986-08-28 | 1989-06-06 | Nippon Pillar Packing Co., Ltd. | Pneumatic pumping device |
US4981418A (en) * | 1989-07-25 | 1991-01-01 | Osmonics, Inc. | Internally pressurized bellows pump |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3219882A1 (de) * | 1982-05-27 | 1983-12-01 | Maschinenfabrik Walter Scheele GmbH & Co KG, 4750 Unna-Massen | Betonpumpe |
US4488592A (en) * | 1983-08-24 | 1984-12-18 | Sperry Corporation | Oscillating coolant pump |
NL8502193A (nl) * | 1985-08-06 | 1987-03-02 | Holthuis Bv | Pompinrichting. |
JPH01232188A (ja) * | 1988-03-11 | 1989-09-18 | Yoshihisa Hamachiyo | ダブルダイヤフラムポンプの脈流防止方法 |
-
1989
- 1989-12-05 JP JP1317206A patent/JPH03179184A/ja active Pending
-
1990
- 1990-08-09 KR KR1019900012232A patent/KR950003063B1/ko not_active IP Right Cessation
- 1990-10-10 US US07/596,718 patent/US5088898A/en not_active Expired - Fee Related
- 1990-11-05 EP EP90312077A patent/EP0431753B1/de not_active Expired - Lifetime
- 1990-11-05 DE DE69011634T patent/DE69011634T2/de not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2463552A (en) * | 1947-03-03 | 1949-03-08 | Donald H Newhall | High-pressure hydraulic system |
US4269569A (en) * | 1979-06-18 | 1981-05-26 | Hoover Francis W | Automatic pump sequencing and flow rate modulating control system |
US4836756A (en) * | 1986-08-28 | 1989-06-06 | Nippon Pillar Packing Co., Ltd. | Pneumatic pumping device |
US4981418A (en) * | 1989-07-25 | 1991-01-01 | Osmonics, Inc. | Internally pressurized bellows pump |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6949202B1 (en) * | 1999-10-26 | 2005-09-27 | Reflectivity, Inc | Apparatus and method for flow of process gas in an ultra-clean environment |
US6827479B1 (en) * | 2001-10-11 | 2004-12-07 | Amphastar Pharmaceuticals Inc. | Uniform small particle homogenizer and homogenizing process |
US20100119394A1 (en) * | 2006-07-11 | 2010-05-13 | Bernhard Frey | Cylinder piston arrangement for a fluid pump or a fluid motor |
US8794938B2 (en) * | 2006-07-11 | 2014-08-05 | Bernhard Frey | Cylinder piston arrangement for a fluid pump or a fluid motor |
US20110150680A1 (en) * | 2009-12-22 | 2011-06-23 | Smith & Nephew, Inc. | Disposable Pumping System and Coupler |
US8337175B2 (en) | 2009-12-22 | 2012-12-25 | Smith & Nephew, Inc. | Disposable pumping system and coupler |
US8932269B2 (en) | 2009-12-22 | 2015-01-13 | Smith & Nephew, Inc. | Disposable pumping system and coupler |
US9341184B2 (en) | 2009-12-22 | 2016-05-17 | Smith & Nephew, Inc. | Disposable pumping system and coupler |
US10408207B2 (en) | 2014-08-04 | 2019-09-10 | Nippon Pillar Packing Co., Ltd. | Bellows pump device |
CN106795876A (zh) * | 2014-08-08 | 2017-05-31 | 日本皮拉工业株式会社 | 波纹管泵装置 |
US10309391B2 (en) * | 2014-08-08 | 2019-06-04 | Nippon Pillar Packing Co., Ltd. | Bellows pump device |
CN106795876B (zh) * | 2014-08-08 | 2019-06-11 | 日本皮拉工业株式会社 | 波纹管泵装置 |
US20170191476A1 (en) * | 2014-08-08 | 2017-07-06 | Nippon Pillar Packing Co., Ltd. | Bellows pump device |
WO2019090388A1 (en) * | 2017-11-10 | 2019-05-16 | Quantum Servo Pumping Technologies Pty Ltd | Pumping systems |
AU2018204487B1 (en) * | 2017-11-10 | 2019-05-30 | Quantum Servo Pumping Technologies Pty Ltd | Pumping systems |
US11913437B2 (en) | 2017-11-10 | 2024-02-27 | Quantum Servo Pumping Technologies Pty Ltd | Pumping systems |
Also Published As
Publication number | Publication date |
---|---|
DE69011634D1 (de) | 1994-09-22 |
KR950003063B1 (ko) | 1995-03-30 |
DE69011634T2 (de) | 1995-01-19 |
KR910012537A (ko) | 1991-08-08 |
EP0431753B1 (de) | 1994-08-17 |
EP0431753A1 (de) | 1991-06-12 |
JPH03179184A (ja) | 1991-08-05 |
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